CN104838211A - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
CN104838211A
CN104838211A CN201280077495.7A CN201280077495A CN104838211A CN 104838211 A CN104838211 A CN 104838211A CN 201280077495 A CN201280077495 A CN 201280077495A CN 104838211 A CN104838211 A CN 104838211A
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CN
China
Prior art keywords
load
side unit
temperature
cold
producing medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201280077495.7A
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Chinese (zh)
Other versions
CN104838211B (en
Inventor
冈野博幸
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of CN104838211A publication Critical patent/CN104838211A/en
Application granted granted Critical
Publication of CN104838211B publication Critical patent/CN104838211B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/77—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by controlling the speed of ventilators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/85—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using variable-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F25B2313/02531—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements during cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F25B2313/02533—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements during heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/029—Control issues
    • F25B2313/0293—Control issues related to the indoor fan, e.g. controlling speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/029—Control issues
    • F25B2313/0294—Control issues related to the outdoor fan, e.g. controlling speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F25B2600/111—Fan speed control of condenser fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F25B2600/112—Fan speed control of evaporator fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/19—Refrigerant outlet condenser temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
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    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
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    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
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    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Signal Processing (AREA)
  • Mathematical Physics (AREA)
  • Fuzzy Systems (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Atmospheric Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

In the present invention, a target condensation temperature and a target evaporation temperature are changed in accordance with the load of a load-side unit (300) as determined using a load detection means (315), and the operating frequency of a compressor (101) and the rotational speed of a blower (106) are controlled so that the condensation temperature determined using a temperature detection means matches the target condensation temperature, and so that the evaporation temperature determined using the temperature detection means matches the target evaporation temperature.

Description

Conditioner
Technical field
The present invention relates to the multiple air conditioner gas control device carrying out the running (mixing running hereinafter referred to as cooling and warming) performing cooling operation by each of multiple stage indoor unit (load-side unit) or heat running, particularly relate to and reduce the control method of power consumption.
Background technology
In the past, there is the conditioner (with reference to patent document 1) making the evaporating temperature of the temperature as the control objectives in kind of refrigeration cycle, condensation temperature variable according to load.The load of air-conditioning of this conditioner by estimating according to the difference of operation mode and design temperature and inlet temperature, the evaporating temperature of the temperature of control objectives, condensation temperature are set to variable value, carry out the running of low compression ratio when underload, reduce power consumption.
In addition, owing to being multiple, therefore multiple stage indoor unit operates under respective loading condition simultaneously, is not the mode of the blowout temperature controlling cold-producing medium for independent indoor set, but controls the condensation temperature of cold-producing medium, evaporating temperature for constant mode.
In this approach, monitor the difference of inlet temperature and design temperature, be judged as that the load of air-conditioning is little below the value that " inlet temperature-design temperature " becomes regulation, if refrigeration, then by the evaporating temperature improved as control objectives, the frequency of compressor is reduced, can power consumption be reduced.In addition, if heat running, then by the condensation temperature reduced as control objectives, frequency is reduced, can power consumption be reduced.
At first technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2012-107840 publication (such as with reference to [0014] ~ [0069], Fig. 1 ~ Figure 10)
Summary of the invention
Invent problem to be solved
But, as the conditioner that can carry out the multiple of cooling and warming mixing running that patent document 1 is recorded, at the capacity according to load control of heat source side heat exchanger, and control as when consistent with the evaporating temperature of target, condensation temperature, if only control the temperature of the side in them, then effect is insufficient.
In addition, if in order to carry out controlling according to the condensation temperature of control objectives, evaporating temperature and operate under the state that condenser, evaporimeter pressure fan rotating speed is separately high, then there are the following problems: compared with the power consumption of compressor, the power consumption of pressure fan relatively increases, consequently, energy-saving effect reduces.
The present invention makes to solve above problem, its object is to provide a kind of conditioner, can carry out cooling and warming mixing running multiple air conditioner gas control device in, control evaporating temperature, condensation temperature both sides temperature and improve energy-saving effect.
For solving the means of problem
Conditioner of the present invention has: heat source side unit, described heat source side unit, the outdoor heat converter with compressor and pressure fan is connected in series by pipe arrangement, and via cold-producing medium supply heat, multiple load-side unit, indoor heat converter and the indoor throttling arrangement of described multiple load-side unit are connected in series by pipe arrangement, and from described heat source side unit via described cold-producing medium supply heat, and cold-producing medium control unit, described cold-producing medium control unit switches the flowing of described cold-producing medium according to operational situation, described heat source side unit and described cold-producing medium control unit are connected in series, described cold-producing medium control unit and described load-side unit are connected in series by pipe arrangement, described load-side unit is connected in parallel by pipe arrangement separately from each other, described load-side unit each in perform cooling operation or heat running, described heat source side unit has the temperature testing organization for the condensation temperature and evaporating temperature obtaining described cold-producing medium, the load detecting mechanism of load when described load-side unit has for obtaining running, according to the load of the described load-side unit using described load detecting mechanism to obtain, change target condensation temperature and the target evaporating temperature of described cold-producing medium, control the operating frequency of described compressor and the rotating speed of described pressure fan, to make: the condensation temperature using described temperature testing organization to obtain is consistent with described target condensation temperature, and, the evaporating temperature using described temperature testing organization to obtain is consistent with described target evaporating temperature.
The effect of invention
According to conditioner of the present invention, can control evaporating temperature, condensation temperature both sides temperature to improve energy-saving effect.
Accompanying drawing explanation
Fig. 1 is the summary construction diagram of an example of the refrigerant loop structure of the conditioner representing embodiments of the present invention.
The refrigerant loop figure of the flowing of cold-producing medium when Fig. 2 is the full heating mode of operation of the conditioner representing embodiments of the present invention.
Fig. 3 be the conditioner representing embodiments of the present invention heat main body operation mode time the refrigerant loop figure of flowing of cold-producing medium.
The refrigerant loop figure of the flowing of cold-producing medium when Fig. 4 is the full cooling operation pattern of the conditioner representing embodiments of the present invention.
The refrigerant loop figure of the flowing of cold-producing medium when Fig. 5 is the refrigeration main body operation mode of the conditioner representing embodiments of the present invention.
Fig. 6 is the key diagram that the pressure fan of the conditioner representing embodiments of the present invention controls.
Detailed description of the invention
Below, with reference to the accompanying drawings embodiments of the present invention are described.
Embodiment
Fig. 1 is the summary construction diagram of an example of the refrigerant loop structure of the conditioner 500 representing embodiments of the present invention.According to Fig. 1, the refrigerant loop structure of conditioner 500 is described.In addition, comprise Fig. 1, in the following figures, the magnitude relationship of each component parts is sometimes different from the situation of reality.
This conditioner 500 is arranged at building or apartment etc., by utilizing the kind of refrigeration cycle (heat pump cycle) making refrigerant circulation, can perform changes in temperature mixing running.Conditioner 500 is made up of heat source side unit 100, cold-producing medium control unit 200 and multiple stage (being two in FIG) load-side unit 300 (300a, 300b).
In addition, heat source side unit 100 is connected with high press fit pipe 402 by low-pressure fitting pipe 401 with cold-producing medium control unit 200, and cold-producing medium control unit 200 is connected with liquid line 406a, 406b by flue 405a, 405b with load-side unit 300, forms kind of refrigeration cycle.
[heat source side unit 100]
Heat source side unit 100 has the function supplying cold energy or heat energy to load-side unit 300.
In addition, in FIG, addition of " a " after the Reference numeral of the several equipment had at " heat source side unit 100 " or " b " illustrates.Further, in the following description, sometimes omit " a ", " b " after being attached to Reference numeral, yes that the equipment of any one comprised in " a ", " b " is described for this situation.
Compressor 101, four-way switching valve 102, open and close valve 105, the outdoor heat converter 103 being provided with pressure fan 106 and reservoir 104 as stream switching mechanism and they be connected in series and form main refrigerant circuit is equipped with in heat source side unit 100.
In addition, the position that the position be connected in series by open and close valve 105a and outdoor heat converter 103a respectively, open and close valve 105b and outdoor heat converter 103b are connected in series is called outdoor heat converter unit.
In addition, in heat source side unit 100, be provided with check-valves 107 ~ 115 thus the flowing of cold-producing medium can be set to fixed-direction.
Low-pressure fitting pipe 401 between cold-producing medium control unit 200 and four-way switching valve 102 is provided with check-valves 112, connecting pipings 403 between four-way switching valve 102 and open and close valve 105 is provided with check-valves 108, the connecting pipings 404 between the merging part of outdoor heat converter 103a and two outdoor heat converter 103a, 103b is provided with check-valves 107a, 107b.
And, connecting pipings 404 between the merging part and cold-producing medium control unit 200 of two outdoor heat converters 103a, 103b is provided with check-valves 109, the high press fit pipe 402 between the merging part and cold-producing medium control unit 200 of two outdoor heat converters 103a, 103b is provided with check-valves 113.
And, low-pressure fitting pipe 401 is connected with the 2nd connecting pipings 121 by the 1st connecting pipings 120 with high press fit pipe 402, described 1st connecting pipings 120 connects the downstream of check-valves 112 and the downstream of check-valves 113, and described 2nd connecting pipings 121 connects the upstream side of check-valves 112 and the upstream side of check-valves 113.
In addition, connecting pipings 403 is connected with the 4th connecting pipings 123 by the 3rd connecting pipings 122 with connecting pipings 404, described 3rd connecting pipings 122 connects the downstream of check-valves 108 and the downstream of check-valves 109, and described 4th connecting pipings 123 connects the upstream side of check-valves 108 and the upstream side of check-valves 109.
1st connecting pipings 120 is provided with only at the check-valves 115 of allowing the circulation of cold-producing medium from low-pressure fitting pipe 401 to the direction of high press fit pipe 402, the 2nd connecting pipings 121 is also provided with only at the check-valves 114 of allowing the circulation of cold-producing medium from low-pressure fitting pipe 401 to the direction of high press fit pipe 402.
In addition, 3rd connecting pipings 122 is provided with and is only allowing the check-valves 110 of circulation of cold-producing medium to the direction of connecting pipings 403 from connecting pipings 404, the 4th connecting pipings 123 is also provided with and is only allowing the check-valves 111 of circulation of cold-producing medium to the direction of connecting pipings 403 from connecting pipings 404.
In addition, in heat source side unit 100, between compressor 101 and four-way switching valve 102, be provided with high pressure sensor 141.In addition, between four-way switching valve 102 and reservoir 104, low pressure sensor 142 is provided with.
Compressor 101, by sucking the gas refrigerant of low-temp low-pressure, compresses this cold-producing medium and makes it to become the gas refrigerant of HTHP, and make cold-producing medium at system Inner eycle thus make operation of air conditioner.Compressor 101 such as can by can frequency conversion (inverter) the type compressor etc. of control capability form.But not being defined in by compressor 101 can the frequency conversion type compressor of control capability, also can be determine rotary speed type compressor or by frequency conversion type with determine the compressor that rotary speed type is combined with.
Four-way switching valve 102 is arranged at the discharge side of compressor 101, switches refrigerant flow path, and control the flowing of cold-producing medium when cooling operation and when heating running, plays function to make outdoor heat converter 103 according to operation mode as evaporimeter or condenser.
Outdoor heat converter 103 carries out heat exchange between thermal medium (such as surrounding air or water etc.) and cold-producing medium, as evaporimeter, cold-producing medium being evaporated when heating running, gasifying, make condensation of refrigerant, liquefaction when cooling operation as condenser (radiator).If outdoor heat converter 103 is air cooling heat exchangers, then in general be provided with pressure fan 106 in the lump, utilize the rotating speed of pressure fan 106, the be supplied to instruction frequency of pressure fan 106, the power consumption of pressure fan 106, the current value etc. that flows through pressure fan 106 controls condensing capacity or evaporability.
In addition, in the present embodiment, two outdoor heat converters 103a, 103b are provided with a pressure fan 106, also pressure fan 106 can be set by each outdoor heat converter 103.
In addition, in the present embodiment, the rotating speed of pressure fan 106 is utilized to control condensing capacity or evaporability.
Reservoir 104 is arranged at the suction side of compressor 101, and has the storage effect of residual refrigerant and the effect of separating refrigerant liquid and gas refrigerant.In addition, as long as reservoir 104 can the container of cold-producing medium of excess of storage.
The upstream portion of open and close valve 105a heat exchanger 103a disposed in the outdoor, the upstream portion of open and close valve 105b heat exchanger 103a disposed in the outdoor, makes cold-producing medium conducting or not conducting by gauge tap.That is, open and close valve 105a, 105b adjusts the flowing of cold-producing medium to outdoor heat converter 103 by gauge tap.
1st connecting pipings 120 connects the high press fit pipe 402 in the downstream of check-valves 113 and the low-pressure fitting pipe 401 in the downstream of check-valves 112.
2nd connecting pipings 121 connects the high press fit pipe 402 of the upstream side of check-valves 113 and the low-pressure fitting pipe 401 of the upstream side of check-valves 112.
In addition, using the merging part of the 2nd connecting pipings 121 and high press fit pipe 402 as merging part a, using the merging part of the 1st connecting pipings 120 and high press fit pipe 402 as merging part b (than merging part a downstream), using the merging part of the 2nd connecting pipings 121 and low-pressure fitting pipe 401 as merging part c, the 1st connecting pipings 120 is illustrated as merging part d (than merging part c downstream) with the merging part of low-pressure fitting pipe 401.
Check-valves 112 is arranged between merging part c and merging part d, and only allows that cold-producing medium is flowing from merging part c to the direction of merging part d.Check-valves 113 is arranged between merging part a and merging part b, and only allows that cold-producing medium is flowing from merging part a to the direction of merging part b.Check-valves 115 is arranged on the 1st connecting pipings 120, and only allows that cold-producing medium is flowing from merging part d to the direction of merging part b.Check-valves 114 is arranged on the 2nd connecting pipings 121, and only allows that cold-producing medium is flowing from merging part c to the direction of merging part a.
3rd connecting pipings 122 connects the high press fit pipe 402 in the downstream of check-valves 109 and the connecting pipings 403 in the downstream of check-valves 108.
4th connecting pipings 123 connects the connecting pipings 404 of the upstream side of check-valves 109 and the connecting pipings 403 of the upstream side of check-valves 108.
In addition, using the merging part of the 4th connecting pipings 123 and connecting pipings 404 as merging part e, using the merging part of the 4th connecting pipings 123 and high press fit pipe 402 as merging part f (than merging part e downstream), using the merging part of the 4th connecting pipings 123 and connecting pipings 403 as merging part g, the 3rd connecting pipings 122 is illustrated as merging part h (than merging part g downstream) with the merging part of connecting pipings 403.
Check-valves 108 is arranged between merging part g and merging part h, and only allows that cold-producing medium is flowing from merging part g to the direction of merging part h.Check-valves 109 is arranged between merging part e and merging part f, and only allows that cold-producing medium is flowing from merging part e to the direction of merging part f.Check-valves 110 is arranged on the 3rd connecting pipings 122, and only allows that cold-producing medium is flowing from merging part f to the direction of merging part h.Check-valves 111 is arranged on the 4th connecting pipings 123, and only allows that cold-producing medium is flowing from merging part e to the direction of merging part g.Between check-valves 107 heat exchanger 103 disposed in the outdoor and merging part, and heat exchanger 103 flows on the direction of merging part e outdoor only to allow cold-producing medium.
High pressure sensor 141 is arranged at the discharge side of compressor 101, and detects the pressure of the cold-producing medium of discharging from compressor 101, and low pressure sensor 142 is arranged at the suction side of compressor 101, and detects the pressure being inhaled into the cold-producing medium of compressor 101.
These high pressure sensors 141 and low pressure sensor 142 as the condensation temperature Tc and evaporating temperature Te for obtaining cold-producing medium described later temperature testing organization and used.
These pressure informations detected by temperature testing organization are sent to the control device 124 of the action controlling conditioner 500, and are used in the control of the switching of the operating frequency of compressor 101, the rotating speed of pressure fan 106 and four-way switching valve 102.
[cold-producing medium control unit 200]
Cold-producing medium control unit 200 between heat source side unit 100 and load-side unit 300, and switches the flowing of cold-producing medium according to the operational situation of load-side unit 300.
In addition, in FIG, addition of " a " after the Reference numeral of the several equipment had at " cold-producing medium control unit 200 " or " b " illustrates.This expression is connected with " the load-side unit 300a " that illustrate below or is connected with " load-side unit 300b ".Further, in the following description, sometimes omit " a ", " b " after being attached to Reference numeral, yes comprises any one equipment be connected with " load-side unit 300a ", " load-side unit 300b " and be described for this situation.
Cold-producing medium control unit 200 is connected with heat source side unit 100 with low-pressure fitting pipe 401 by high press fit pipe 402, is connected with flue 405 by liquid line 406 with load-side unit 300.Gas-liquid separator 211, the 1st open and close valve 212 (the 1st open and close valve 212a, 212b), the 2nd open and close valve 213 (the 2nd open and close valve 213a, 213b), Section 1 stream device 214, Section 2 stream device the 215, the 1st refrigerant heat exchanger 216 and the 2nd refrigerant heat exchanger 217 is equipped with in cold-producing medium control unit 200.In addition, the primary side of the 1st refrigerant heat exchanger 216 and the 2nd refrigerant heat exchanger 217 is provided with connecting pipings 221, secondary side is provided with connecting pipings 220.In addition, 1st refrigerant heat exchanger 216 and the primary side of the 2nd refrigerant heat exchanger 217 are the sides of the liquid refrigerant flowing be separated by gas-liquid separator 211, and secondary side is the side that overcooled, cold-producing medium for carrying out the cold-producing medium flowing through primary side flow via Section 1 stream device 214 and Section 2 stream device 215.
Gas-liquid separator 211 is arranged at the connecting portion of high press fit pipe 402 and connecting pipings 221, and has and will flow through high press fit pipe 402 and the two phase refrigerant come is separated into the function of gas refrigerant and liquid refrigerant.Be supplied to the 1st open and close valve 212 by the isolated gas refrigerant of gas-liquid separator 211 via connecting pipings 221, liquid refrigerant is supplied to the 1st refrigerant heat exchanger 216.
1st open and close valve 212 for controlling the supply to the cold-producing medium of load-side unit 300 according to operation mode, and is arranged between connecting pipings 221 and flue 405.That is, a side of the 1st open and close valve 212 is connected with gas-liquid separator 211, and the opposing party is connected with the indoor heat converter 312 of load-side unit 300, and is made cold-producing medium conducting or not conducting by gauge tap.
2nd open and close valve 213 for controlling the supply to the cold-producing medium of load-side unit 300 according to operation mode, and is arranged between connecting pipings 220 and flue 405.That is, a side of the 2nd open and close valve 213 is connected with the 1st refrigerant heat exchanger 216, and the opposing party is connected with the indoor heat converter 312 of load-side unit 300, and is made cold-producing medium conducting or not conducting by gauge tap.
Section 1 stream device 214 is arranged between the 1st refrigerant heat exchanger 216 of connecting pipings 221 and the 2nd refrigerant heat exchanger 217, and has the function as pressure-reducing valve or expansion valve, makes cold-producing medium reduce pressure and expand.This Section 1 stream device 214 can control as aperture is variable, such as, can form by utilizing the cheap refrigerant flow regulating mechanism etc. such as the volume control device of the precision of electronic expansion valve, capillary.
Section 2 stream device 215 be arranged on connecting pipings 220, the upstream side of the secondary side of the 2nd refrigerant heat exchanger 217, there is the function as pressure-reducing valve or expansion valve, make cold-producing medium reduce pressure and expand.In the same manner as Section 1 stream device 214, this Section 2 stream device 215 can control as aperture is variable, such as, can form by utilizing the cheap refrigerant flow regulating mechanism etc. of the careful volume control device, capillary etc. of electronic expansion valve.
1st refrigerant heat exchanger 216 performs heat exchange flowing through between the cold-producing medium of primary side and the cold-producing medium flowing through secondary side.
2nd refrigerant heat exchanger 217 performs heat exchange flowing through between the cold-producing medium of primary side and the cold-producing medium flowing through secondary side.
Cold-producing medium control unit 200 utilizes the 1st refrigerant heat exchanger 216 and the 2nd refrigerant heat exchanger 217 to carry out heat exchange flowing through between the cold-producing medium of primary side and the cold-producing medium flowing through secondary side, and carries out the supercooling of the cold-producing medium flowing through primary side.
In addition, the aperture of Section 1 stream device 214 is utilized to control bypass amount, to make can carry out suitable supercooling in the primary side outlet of the 1st refrigerant heat exchanger 216, the aperture of Section 2 stream device 215 is utilized to control bypass amount, to make carry out suitable supercooling in the primary side outlet of the 2nd refrigerant heat exchanger 217.
[load-side unit 300]
Load-side unit 300 accepts from the cold energy of heat source side unit 100 or the supply of heat energy and bears refrigeration load or heat load.
In addition, in FIG, after the Reference numeral of each equipment had at " load-side unit 300a " additional " a ", and after the Reference numeral of each equipment had at " load-side unit 300b ", additional " b " illustrates.And, in the following description, sometimes omit " a ", " b " after Reference numeral, certainly load-side unit 300a, load-side unit 300b either party in all there is each equipment.
Be equipped with indoor heat converter 312 (indoor heat converter 312a, 312b) and indoor throttling arrangement 311 (indoor throttling arrangement 311a, 311b) with being connected in series in load-side unit 300.
In addition, temperature sensor 313 (temperature sensor 313a, 313b) is provided with between indoor heat converter 312 and the 1st open and close valve 212, the 2nd open and close valve 213, between indoor throttling arrangement 311 and indoor heat converter 312, be provided with temperature sensor 314 (temperature sensor 314a, 314b), in indoor heat converter 312 or near it, be provided with temperature sensor 315 (temperature sensor 315a, 315b).
In addition, also can arrange near indoor heat converter 312 be used for the illustrated pressure fan of the air fed omission of indoor heat converter 312.
Indoor throttling arrangement 311 has the function as pressure-reducing valve, expansion valve, cold-producing medium is reduced pressure and expands.This indoor throttling arrangement 311 can control as aperture is variable, such as, can form by utilizing the cheap refrigerant flow regulating mechanism etc. such as the volume control device of the precision of electronic expansion valve, capillary.
Indoor heat converter 312 carries out heat exchange between thermal medium (such as surrounding air or water etc.) and cold-producing medium, when heating running as condenser (radiator) by condensation of refrigerant, liquefaction, make as evaporimeter when cooling operation cold-producing medium evaporate, gasification.In general indoor heat converter 312 is provided with in the lump and omits illustrated pressure fan, and utilize the rotating speed of pressure fan, be supplied to the instruction frequency of pressure fan, the power consumption of pressure fan, the current value etc. that flows through pressure fan control condensing capacity or evaporability.
In addition, in the present embodiment, the rotating speed of pressure fan is utilized to control condensing capacity or evaporability.
The temperature of the refrigerant piping between temperature sensor 313 sensing chamber inside heat exchanger the 312 and the 1st open and close valve 212, the 2nd open and close valve 213.
The temperature of the refrigerant piping in temperature sensor 314 sensing chamber between throttling arrangement 311 and indoor heat converter 312.
Temperature sensor 315 detects the load-side inlet temperature Ta of the room air in indoor heat converter 312 described later.
In addition, be sent to the control device 124 of the action controlling conditioner 500 by these as the information (temperature information) that the temperature sensor 313 ~ 315 of load detecting mechanism detects and be used in the control of various actuator.That is, from the Information Pull of temperature sensor 313 ~ 315 in the control being arranged on the aperture of the indoor throttling arrangement 311 in load-side unit 300, the rotating speed omitting illustrated pressure fan etc.
In addition, as long as the refrigerant compression of suction can be become high pressure conditions, without particular limitation of type by compressor 101.Such as, can utilize back and forth, vortex, all kinds such as rolling or spiral to be to form compressor 101.In addition, the kind being used in the cold-producing medium of conditioner 500 without particular limitation of, such as can use the alternative refrigerant that natural refrigerant, HFC410A, HFC407C, the HFC404A etc. such as carbon dioxide, hydrocarbon, helium are not chloride, or any one in the freon class cold-producing medium such as R22, R134a of being used in existing product.
In addition, in FIG, so that the control device 124 of the action controlling conditioner 500 is mounted in the situation of heat source side unit 100 for exemplifying, but also can be arranged in either party in cold-producing medium control unit 200 or load-side unit 300.In addition, also control device 124 can be arranged on the outside of heat source side unit 100, cold-producing medium control unit 200 and load-side unit 300.In addition, also control device 124 can be divided into multiple according to function, and be arranged on heat source side unit 100, cold-producing medium control unit 200, load-side unit 300 each in.In this case, by wireless or wiredly connect each control device, and can be set in advance and can communicate.
Here, the motion of each pattern that conditioner 500 performs is described.
In conditioner 500, such as receive from remote controller disposed in the interior etc. cooling operation request, heat running and ask and carry out operation of air conditioner, ask existence 4 kinds of operation modes according to these.As 4 kinds of operation modes, have: all load-side unit 300 is all the full cooling operation pattern of cooling operation request, cooling operation request and heat running request and exist and the refrigeration main body operation mode being judged as utilizing the load of cooling operation process many (each load sum performing the load-side unit 300 of cooling operation is larger than performing each load sum heating the load-side unit 300 of running) simultaneously, cooling operation request and heat running request exist simultaneously and be judged as utilizing the load heating running process many (each load sum that execution heats the load-side unit 300 of running is larger than each load sum of the load-side unit 300 performing cooling operation) heat main body operation mode, and all load-side unit 300 is all the full heating mode of operation heating running request.
[full heating mode of operation]
The refrigerant loop figure of the flowing of cold-producing medium when Fig. 2 is the full heating mode of operation of the conditioner 500 representing embodiments of the present invention.Motion when according to Fig. 2 the full heating mode of operation of conditioner 500 being described.
The cold-producing medium of low-temp low-pressure is compressed by compressor 101, becomes the gas refrigerant of HTHP and discharges.The gas refrigerant of HTHP of discharging from compressor 101 is via four-way switching valve 102, and conducting, through check-valves 115, flows through high press fit pipe 402 and flows out from heat source side unit 100, and arriving cold-producing medium control unit 200.
The gas refrigerant flowing into cold-producing medium control unit 200 flows into gas-liquid separator 211, flows through connecting pipings 221 and arrives the 1st open and close valve 212.Now, the 1st open and close valve 212 is open, and the 2nd open and close valve 213 is closed.Then, conducting through the HTHP of the 1st open and close valve 212 gas refrigerant gas coming through pipe 405 and flow out from cold-producing medium control unit 200, and arrive load-side unit 300.
Flow into the gas refrigerant inflow indoor heat exchanger 312 (indoor heat converter 312a and indoor heat converter 312b) of load-side unit 300.Because indoor heat converter 312 is as condenser working, cold-producing medium and ambient air carry out heat exchange and condensation, liquefaction.Now, by cold-producing medium heat release towards periphery, the indoor air-conditioning object space that waits is heated.Afterwards, the liquid refrigerant that heat exchanger 312 flows out indoor is depressurized in indoor throttling arrangement 311 (indoor throttling arrangement 311a and indoor throttling arrangement 311b), flow through liquid line 406 (liquid line 406a and liquid line 406b) and flow out from load-side unit 300, and arriving cold-producing medium control unit 200.
The liquid refrigerant conducting flowing into cold-producing medium control unit 200, through Section 2 stream device 215, flows through connecting pipings 220 and arrives low-pressure fitting pipe 401.Then, liquid refrigerant flows through low-pressure fitting pipe 401 and flows out from cold-producing medium control unit 200, returns heat source side unit 100.
The cold-producing medium conducting returning heat source side unit 100 is through check-valves 114, check-valves 110 and arrive outdoor heat converter 103 (outdoor heat converter 103a and outdoor heat converter 103b).Now, open and close valve 105 is opened and closed.Because outdoor heat converter 103 is as evaporator operation, cold-producing medium and ambient air carry out heat exchange, and cold-producing medium evaporates and gasifies.Afterwards, heat exchanger 103 effluent air cold-producing medium flows into reservoir 104 via four-way switching valve 102 outdoor.Then, compressor 101 sucks the gas refrigerant in reservoir 104, by making it at system Inner eycle thus forming kind of refrigeration cycle.
Conditioner 500 performs full heating mode of operation according to above flow process.
When full heating mode of operation, it is consistent with target condensation temperature Tcm that the operating frequency of compressor 101 is controlled as the condensation temperature Tc calculated according to (cold-producing medium that compressor 101 is discharged) discharge pressure, and the high pressure sensor 141 that described discharge pressure is used as temperature testing organization detects.In addition, it is consistent with target evaporating temperature Tem that the rotating speed of pressure fan 106 is controlled as the evaporating temperature Te calculated according to (cold-producing medium that compressor 101 sucks) suction pressure, and described suction pressure is detected by the low pressure sensor 142 as temperature testing organization.
Therefore, when the operating frequency of compressor 101 is set to constant and heat load become large time, condensation temperature Tc reduce.Therefore, by improving target condensation temperature Tcm and making the operating frequency increase of compressor 101 make condensation temperature Tc consistent with this Tcm, the action improving heating capacity is become.
On the contrary, when the operating frequency of compressor 101 is set to constant and heat load diminish time, condensation temperature Tc rise.Therefore, make condensation temperature Tc consistent with this Tcm by reducing target condensation temperature Tcm and making the operating frequency of compressor 101 reduce, become the action reducing heating capacity, can power consumption be reduced.
In addition, the load-side inlet temperature Ta of the room air in the indoor heat converter 312 detected by the temperature sensor 315 as load detecting mechanism and the difference Δ Th of design temperature To is to obtain the load of load-side unit 300, when heating load and diminishing, load-side inlet temperature Ta and design temperature To is close.Therefore, be judged as that load is little when heating value Δ Tho little (the Δ Th< Δ Tho) of the ratio of the temperature difference Δ Th=To-Ta in running regulation, target condensation temperature initial value Tcm0 is changed to target condensation temperature change value Tcm1.Now, Tcm1 both can be fixing value, also can become the function of temperature difference Δ Th, but Tcm0>Tcm1.Here, when multiple load-side unit 300 operates, Ta both can be arithmetic average, weighted average that also can be corresponding to ability.In addition, also can by the load-side unit 300 of connection, the load-side unit 300 that obtains maximum temperature difference Δ Th representatively.
In any one situation, because Tcm0 becomes Tcm1 (<Tcm0), and the operating frequency of compressor 101 declines along with target, therefore can both reduce power consumption.
In addition, outdoor heat converter 103 is configured to carry out the flowing of control flow check to the cold-producing medium of outdoor heat converter 103 by the on-off action of open and close valve 105.In the present embodiment, as shown in Figure 2, outdoor heat converter 103 is set to these two segmenting structures of outdoor heat converter 103a, 103b, but also by arranging open and close valve 105 and check-valves 107 in the front and back of outdoor heat converter 103, the structure that two segmentations are above can be set to.
That is, the switch of each open and close valve 105 is controlled according to the load of load-side unit 300, and select the volume (quantity of the outdoor heat converter 103 that cold-producing medium is flowed into) carrying out the outdoor heat converter 103 of heat exchange, when Segmentation Number increases, the quantity can carrying out this selection also increases.
In addition, when heating load hour, the volume of outdoor heat converter 103 can be selected maximum in advance.That is, in fig. 2, open and close valve 105a and 105b is set to open state to strengthen heat exchange volume.Like this, when heating load hour, even if be set to minimum by the rotating speed of pressure fan 106, evaporating temperature Te also can be made consistent with target evaporating temperature Tem, therefore, it is possible to reduce the power consumption of pressure fan 106.
According to more than, it is consistent with target condensation temperature Tcm that the operating frequency of compressor 101 is controlled as condensation temperature Tc, and it is consistent with target evaporating temperature Tem that the rotating speed of pressure fan 106 is controlled as evaporating temperature Te.
Therefore, when the operating frequency of compressor 101 is set to constant and heat load diminish time, condensation temperature Tc rise.Therefore, make condensation temperature Tc consistent with this Tcm by reducing target condensation temperature Tcm and making the operating frequency of compressor 101 reduce, become the action reducing heating capacity, can power consumption be reduced.
In addition, when heating load hour, because load-side inlet temperature Ta and design temperature To is close, be judged as that load is little when heating the temperature difference Δ Th=To-Ta in running and being less than the value Δ Tho of regulation, target condensation temperature initial value Tcm0 is changed to target condensation temperature change value Tcm1 (<Tcm0).Like this, because the operating frequency of compressor 101 declines along with target, power consumption can be reduced.
In addition, when heating load hour, select maximum in advance by the volume of outdoor heat converter 103, thus when heating load hour, even if the rotating speed of pressure fan 106 is set to minimum, also evaporating temperature Te can be made consistent with target evaporating temperature Tem, therefore, it is possible to reduce the power consumption of pressure fan 106.
In addition, when heating load and being large, by making the operating frequency of compressor 101 reduce, also can reduce power consumption, but also decline due to heating capacity simultaneously, so it is little and without the need to the situation of heating capacity, implement running efficiently at this moment to judge to heat load.
In addition, in the present embodiment, be set to the rotating speed of pressure fan 106 for air-cooled type, also can monitor water pump controlling value (frequency, power consumption, electric current) and control open and close valve 105a, 105b in water-cooled.
By controlling according to upper type, the conditioner 500 of good energy-conserving effect can be obtained.
In addition, as the running request being supplied to conditioner 500, at cooling operation with heat running and exist simultaneously, and when being judged as utilizing the load heating running process larger, operation mode becomes and heats main body operation mode.
[heating main body operation mode]
Fig. 3 be the conditioner 500 representing embodiments of the present invention heat main body operation mode time the refrigerant loop figure of flowing of cold-producing medium.According to Fig. 3 illustrate conditioner 500 heat main body operation mode time motion.Here, illustrate from load-side unit 300a have the request of heating, from load-side unit 300b have refrigeration request time heat main body operation mode.
In addition, because the flowing of the cold-producing medium to the load-side unit 300a having the request of heating is identical with during full heating mode of operation, therefore omit the description.
The liquid refrigerant flowing through liquid line 406a applies supercooling by the 2nd refrigerant heat exchanger 217, afterwards, flows through liquid line 406b and arrives the load-side unit 300b freezing and ask.The liquid refrigerant flowing into load-side unit 300b is reduced pressure by indoor throttling arrangement 311b.The liquid refrigerant inflow indoor heat exchanger 312b reduced pressure by indoor throttling arrangement 311b.Because indoor heat converter 312b is as evaporator operation, therefore liquid refrigerant and ambient air carry out heat exchange, evaporate and gasify.Now, by cold-producing medium from around absorbing heat, indoor cooled.Afterwards, from the conducting of load-side unit 300b effluent air cold-producing medium through the 2nd open and close valve 213b, and connecting pipings 220 is flowed through.This gas refrigerant with in order to carry out in the 2nd refrigerant heat exchanger 217 supercooling and conducting through Section 1 stream device 214 and Section 2 stream device 215 and the cold-producing medium flowing through connecting pipings 220 and come to collaborate and after becoming gas-liquid two-phase, flow through low-pressure fitting pipe 401 and flow out from cold-producing medium control unit 200, and returning heat source side unit 100.
The gas-liquid two-phase cold-producing medium conducting returning heat source side unit 100 is through check-valves 114, check-valves 110 and arrive outdoor heat converter 103 (outdoor heat converter 103a and outdoor heat converter 103b).Now, open and close valve 105a is open.Because outdoor heat converter 3 is as evaporator operation, therefore gas-liquid two-phase cold-producing medium and ambient air carry out heat exchange, and cold-producing medium evaporates and gasifies.Afterwards, heat exchanger 103 effluent air cold-producing medium flows into reservoir 104 via four-way switching valve 102 outdoor.Then, compressor 101 sucks the gas refrigerant in reservoir 104, forms kind of refrigeration cycle by making it at system Inner eycle.Conditioner 500 performs according to above flow process and heats main body operation mode.
Heating in main body operation mode, in the same manner as full heating mode of operation, by changing target condensation temperature Tcm and target evaporating temperature Tem according to heating load, power consumption can be reduced.
By controlling as above, the conditioner 500 of good energy-conserving effect can be obtained.
In addition, in the present embodiment, show the example that heat source side unit 100 is, cold-producing medium control unit 200 is, load-side unit 300 is two, but the number of units of each unit without particular limitation of.In addition, in the present embodiment, be illustrated for the situation applying the present invention to conditioner 500, but the use kind of refrigeration cycle that also can apply the present invention to comprise refrigeration system is in the other system forming refrigerant loop.
[full cooling operation pattern]
The refrigerant loop figure of the flowing of cold-producing medium when Fig. 4 is the full cooling operation pattern of the conditioner 500 representing embodiments of the present invention.Motion during the full cooling operation pattern of conditioner 500 is described simply according to Fig. 4.
The cold-producing medium of low-temp low-pressure is compressed by compressor 101, becomes the gas refrigerant of HTHP and discharges.The gas refrigerant of HTHP of discharging from compressor 101 is via four-way switching valve 102, and conducting is through check-valves 108 and arrive open and close valve 105.Now, open and close valve 105 is opened.Then, conducting is flowed to outdoor heat converter 103 through the gas refrigerant of open and close valve 105.Because outdoor heat converter 103 is as condenser working, therefore gas refrigerant and ambient air carry out heat exchange and condensation, liquefaction.Afterwards, the liquid refrigerant of the high pressure of heat exchanger 103 outflow outdoor flows through connecting pipings 404, and conducting, through check-valves 109 and check-valves 113, flows through high press fit pipe 402 and flows out from heat source side unit 100, and arrive cold-producing medium control unit 200.
The liquid refrigerant flowing into cold-producing medium control unit 200 flows into gas-liquid separator 211, and flows into the primary side of the 1st refrigerant heat exchanger 216.Therefore, liquid refrigerant applies supercooling by the cold-producing medium of the secondary side flowing through the 1st refrigerant heat exchanger 216.This degree of supercooling becomes large liquid refrigerant and become intermediate pressure by throttling in Section 1 stream device 214.Then, this liquid refrigerant flows through the 2nd refrigerant heat exchanger 217, is applied in supercooling further.Afterwards, liquid refrigerant is shunted, and a part flows through liquid line 406 (liquid line 406a and liquid line 406b) and flows out from cold-producing medium control unit 200, and arrives load-side unit 300.
The liquid refrigerant flowing into load-side unit 300 is reduced pressure by indoor throttling arrangement 311 (indoor throttling arrangement 311a and indoor throttling arrangement 311b), becomes the gas-liquid two-phase cold-producing medium of low temperature.The gas-liquid two-phase cold-producing medium inflow indoor heat exchanger 312 (indoor heat converter 312a and indoor heat converter 312b) of this low temperature.Because indoor heat converter 312 is as evaporator operation, therefore cold-producing medium and ambient air carry out heat exchange, evaporate and gasify.Now, by cold-producing medium from around absorbing heat, indoor cooled.Afterwards, heat exchanger 312 effluent air flow of refrigerant flows out load-side unit 300 through flue 405 (flue 405a and flue 405b) indoor, and arrives cold-producing medium control unit 200.
The gas refrigerant flowing into cold-producing medium control unit 200 arrives the 2nd open and close valve 213.Now, the 2nd open and close valve 213 is open, and the 1st open and close valve 212 is closed.Then, conducting through the 2nd open and close valve 213 gas refrigerant with in order to carry out supercooling and conducting through Section 1 stream device 214 and Section 2 stream device 215 and after the cold-producing medium flowing through connecting pipings 220 and come collaborates in the 2nd refrigerant heat exchanger 217, flow through low-pressure fitting pipe 401 and flow out from cold-producing medium control unit 200, and returning heat source side unit 100.
The gas refrigerant conducting returning heat source side unit 100, through check-valves 112, flows into reservoir 104 via four-way switching valve 102.Then, compressor 101 sucks the gas refrigerant in reservoir 104, by making it to form kind of refrigeration cycle at system Inner eycle.Conditioner 500 performs full cooling operation pattern according to above flow process.
When full cooling operation pattern, it is consistent with target evaporating temperature Tem that the operating frequency of compressor 101 is controlled as the evaporating temperature Te calculated according to (cold-producing medium that compressor 101 sucks) suction pressure, and described suction pressure is detected by the low pressure sensor 142 as temperature testing organization.In addition, it is consistent with target condensation temperature Tcm that the rotating speed of pressure fan 106 is controlled as the condensation temperature Tc calculated according to (cold-producing medium that compressor 101 is discharged) discharge pressure, and described discharge pressure is detected by the high pressure sensor 141 as temperature testing organization.
Therefore, when the operating frequency of compressor 101 being set to constant and refrigeration load and becoming large, evaporating temperature Te rises.Therefore, by reducing target evaporating temperature Tem and making the operating frequency increase of compressor 101 make evaporating temperature Te consistent with this Tem, thus the action reducing refrigerating capacity is become.
On the contrary, when the operating frequency of compressor 101 is set to constant and refrigeration load diminishes time, evaporating temperature Te reduce.Therefore, make evaporating temperature Te consistent with this Tem by improving target evaporating temperature Tem and making the operating frequency of compressor 101 reduce, thus become the action improving refrigerating capacity, can power consumption be reduced.
The load-side inlet temperature Ta of the room air that the temperature sensor 315 being used as load detecting mechanism detects and the difference Δ Tc of design temperature To is to obtain the load of load-side unit 300, when heating load and diminishing, load-side inlet temperature Ta and design temperature To is close.Therefore, than value Δ Tro little (the Δ Tr< Δ Tro) that specify, temperature difference Δ Tr=Ta-To when cooling operation is judged as that load is little, target evaporating temperature initial value Tem0 is changed to target evaporating temperature change value Tem1.Now, Tem1 both can be fixing value, also can become the function of temperature difference Δ Tr, but Tem0<Tem1.Here, when multiple load-side unit 300 operates, Ta both can be arithmetic average, weighted average that also can be corresponding to ability.In addition, also can by the load-side unit 300 of connection, the load-side unit 300 that obtains maximum temperature difference Δ Tr representatively.In any one situation, because Tem0 becomes Tem1 (>Tem0), and the operating frequency of compressor 101 declines along with target, therefore can both reduce power consumption.
In addition, refrigeration load hour, the volume of outdoor heat converter 103 can be selected maximum in advance.That is, in the diagram, open and close valve 105a and 105b is set to open state to strengthen heat exchange volume.Like this, when refrigeration load hour, even if consistent with target condensation temperature Tcm owing to the rotating speed of pressure fan 106 to be set to the minimum condensation temperature Tc that also can make, therefore, it is possible to reduce the power consumption of pressure fan 106.
According to more than, it is consistent with target evaporating temperature Tem that the operating frequency of compressor 101 is controlled as evaporating temperature Te, and it is consistent with target condensation temperature Tcm that the rotating speed of pressure fan 106 is controlled as condensation temperature Tc.
Therefore, when the operating frequency of compressor 101 is set to constant and refrigeration load diminishes time, evaporating temperature Te reduce.Therefore, make evaporating temperature Te consistent with this Tem by improving target evaporating temperature Tem and making the operating frequency of compressor 101 reduce, thus become the action reducing refrigerating capacity, can power consumption be reduced.
In addition, when refrigeration load hour, because load-side inlet temperature Ta and design temperature To is close, be judged as that load is little temperature difference Δ Tr=To-Ta in cooling operation is less than the value Δ Tro of regulation, target evaporating temperature initial value Tem0 is changed to target evaporating temperature change value Tem1 (>Tem0).Like this, because the operating frequency of compressor 101 declines along with target, therefore, it is possible to reduce power consumption.
In addition, when refrigeration load hour, select maximum in advance by the volume of outdoor heat converter 103, thus when refrigeration load hour, even if the rotating speed of pressure fan 106 is set to minimum, also condensation temperature Tc can be made consistent with target condensation temperature Tcm, therefore, it is possible to reduce the power consumption of pressure fan 106.
In addition, when refrigeration load is large, by making the operating frequency of compressor 101 reduce, also can reduce power consumption, but also decline due to refrigerating capacity simultaneously, so judge that refrigeration load is little and without the need to the situation of refrigerating capacity, implement running efficiently at this moment.
By controlling according to upper type, the conditioner 500 of good energy-conserving effect can be obtained.
[refrigeration main body operation mode]
The refrigerant loop figure of the flowing of cold-producing medium when Fig. 5 is the refrigeration main body operation mode of the conditioner 500 representing embodiments of the present invention.Motion during the refrigeration main body operation mode of conditioner 500 is described according to Fig. 5.Here, illustrate from load-side unit 300a and have refrigeration request, have refrigeration main body operation mode when heating request from load-side unit 300b.
The cold-producing medium of low-temp low-pressure is compressed by compressor 101, becomes the gas refrigerant of HTHP and discharges.The gas refrigerant of HTHP of discharging from compressor 101 is via four-way switching valve 102, and conducting is through check-valves 108 and arrive open and close valve 105.Now, open and close valve 105 is opened.Then, conducting is flowed to outdoor heat converter 103 through the gas refrigerant of open and close valve 105.Because outdoor heat converter 103 is as condenser working, therefore gas refrigerant and ambient air carry out heat exchange and condensation, liquefaction.Afterwards, the gas-liquid two-phase flow of refrigerant of the high pressure of heat exchanger 103 outflow is outdoor through connecting pipings 404, and conducting, through check-valves 109 and check-valves 113, flows through high press fit pipe 402 and flows out from heat source side unit 100, and arriving cold-producing medium control unit 200.
The gas-liquid two-phase cold-producing medium flowing into cold-producing medium control unit 200 flows into gas-liquid separator 211, is separated into gas refrigerant and liquid refrigerant by gas-liquid separator 211.After separation, gas refrigerant flows out from gas-liquid separator 211, flows through connecting pipings 221 and arrives the 1st open and close valve 212.Now, the 1st open and close valve 212a closes, and the 1st open and close valve 212b is open.Then, conducting, through the gas refrigerant gas coming through pipe 405b of the 1st open and close valve 212b, flows into load-side unit 300b.The gas refrigerant flowing into load-side unit 300b is heated conditioned space by heat release towards periphery in indoor heat converter 312b, and self condensation, liquefaction.Now, by cold-producing medium from around absorbing heat, indoor cooled.Afterwards, the liquid refrigerant that heat exchanger 312b flows out indoor becomes intermediate pressure by indoor throttling arrangement 311b throttling.
Flow through liquid line 406b by the liquid refrigerant of the intermediate pressure of indoor throttling arrangement 311b throttling and flow into the 2nd refrigerant heat exchanger 217.Therefore, with by gas-liquid separator 211 be separated, flow through the 1st refrigerant heat exchanger 216, conducting through Section 1 stream device 214 and the liquid refrigerant flowing into the 2nd refrigerant heat exchanger 217 collaborate.Then, the liquid refrigerant being increased degree of supercooling by the 2nd refrigerant heat exchanger 217 further flows through liquid line 406a and flows out from cold-producing medium control unit 200, arrives load-side unit 300a.
The liquid refrigerant flowing into load-side unit 300 is reduced pressure by indoor throttling arrangement 311a, becomes the gas-liquid two-phase cold-producing medium of low temperature.The gas-liquid two-phase cold-producing medium inflow indoor heat exchanger 312a of this low temperature.Because indoor heat converter 312a is as evaporator operation, therefore cold-producing medium and ambient air carry out heat exchange, evaporate and gasify.Now, by cold-producing medium from around absorbing heat, indoor cooled.Afterwards, heat exchanger 312a effluent air flow of refrigerant flows out from load-side unit 300 through flue 405a indoor, arrives cold-producing medium control unit 200.
The gas refrigerant flowing into cold-producing medium control unit 200 arrives the 2nd open and close valve 213.Now, the 2nd open and close valve 213a is open, and the 2nd open and close valve 213b closes.Then, conducting through the 2nd open and close valve 213a gas refrigerant with in order to carry out supercooling and conducting through Section 1 stream device 214 and Section 2 stream device 215 and after the cold-producing medium flowing through connecting pipings 220 and come collaborates in the 2nd refrigerant heat exchanger 217, flow through low-pressure fitting pipe 401 and flow out from cold-producing medium control unit 200, and returning heat source side unit 100.
The gas refrigerant conducting returning heat source side unit 100, through check-valves 112, flows into reservoir 104 via four-way switching valve 102.Then, compressor 101 sucks the gas refrigerant in reservoir 104, by making it to form kind of refrigeration cycle at system Inner eycle.Conditioner 500 performs refrigeration main body operation mode according to above flow process.
During refrigeration subject mode, the rotating speed of pressure fan 106 is controlled by head for target condensation temperature Tcm.
When heating load hour, heat load-side inlet temperature Ta in running and design temperature To close.Therefore, in the same manner as full heating mode of operation, be judged as that load is little when temperature difference Δ Th=To-Ta is less than the value Δ Tho of regulation, target condensation temperature initial value Tcm0 is changed to target condensation temperature change value Tcm1.Now, Tcm1 both can be fixing value, also can become the function of temperature difference Δ T, but Tcm0>Tcm1.Here, when multiple load-side unit 300 operates, Ta both can be arithmetic average, also can be the weighted average corresponding to ability.In addition, also can by the load-side unit 300 of connection, the load-side unit 300 that obtains maximum temperature difference Δ Tc representatively.In any one situation, Tcm0 becomes Tcm1 (<Tcm0).
Now, the volume of outdoor heat converter 103 implements the control of open and close valve 105b according to target condensation temperature Tcm.By the heat transfer area reducing outdoor heat converter 103, condensation temperature Tc is maintained higher, but when load is little, owing to needing the rotating speed increasing pressure fan 106, therefore preferably increase the heat transfer area of outdoor heat converter 103.
Fig. 6 is the key diagram that the pressure fan of the conditioner representing embodiments of the present invention controls.
Such as, as shown in Figure 6, control is: when being judged as heating load and being large, open and close valve 105b is closed, reduce the heat transfer area of outdoor heat converter 103 and the rotating speed of pressure fan 106 is reduced, when being judged as heating load and being little, open and close valve 105b is open, strengthen the heat transfer area of outdoor heat converter 103 and the rotating speed of pressure fan 106 is reduced.
In addition, in either case, open and close valve 105a all openings.
By controlling according to upper type, the conditioner 500 of good energy-conserving effect can be obtained.
Description of reference numerals
100 heat source side unit, 101 compressors, 102 four-way switching valves, 103 outdoor heat converters, 103a outdoor heat converter, 103b outdoor heat converter, 104 reservoirs, 105 open and close valves, 105a open and close valve, 105b open and close valve, 106 pressure fan, 107 check-valves, 107a check-valves, 107b check-valves, 108 check-valves, 109 check-valves, 110 check-valves, 111 check-valves, 112 check-valves, 113 check-valves, 114 check-valves, 115 check-valves, 120 the 1st connecting pipings, 121 the 2nd connecting pipings, 122 the 3rd connecting pipings, 123 the 4th connecting pipings, 124 control device, 141 high pressure sensors, 142 low pressure sensors, 200 cold-producing medium control units, 211 gas-liquid separators, 212 the 1st open and close valves, 212a the 1st open and close valve, 212b the 1st open and close valve, 213 the 2nd open and close valves, 213a the 2nd open and close valve, 213b the 2nd open and close valve, 214 Section 1 stream devices, 215 Section 2 stream devices, 216 the 1st refrigerant heat exchanger, 217 the 2nd refrigerant heat exchanger, 220 connecting pipings, 221 connecting pipings, 300 load-side unit, 300a load-side unit, 300b load-side unit, 311 indoor throttling arrangements, the indoor throttling arrangement of 311a, the indoor throttling arrangement of 311b, 312 indoor heat converters, 312a indoor heat converter, 312b indoor heat converter, 313 temperature sensors, 313a temperature sensor, 313b temperature sensor, 314 temperature sensors, 314a temperature sensor, 314b temperature sensor, 315 temperature sensors, 315a temperature sensor, 315b temperature sensor, 300 load-side unit, 300a load-side unit, 300b load-side unit, 401 low-pressure fitting pipes, 402 high press fit pipes, 403 connecting pipings, 404 connecting pipings, 405 flues, 405a flue, 405b flue, 406 liquid lines, 406a liquid line, 406b liquid line, 500 conditioners, a merging part, b merging part, c merging part, d merging part, e merging part, f merging part, g merging part, h merging part.

Claims (7)

1. a conditioner, has:
Heat source side unit, described heat source side unit, compressor and the outdoor heat converter with pressure fan be connected in series by pipe arrangement, and via cold-producing medium supply heat;
Multiple load-side unit, indoor heat converter and the indoor throttling arrangement of described multiple load-side unit are connected in series by pipe arrangement, and described multiple load-side unit is supplied to heat from described heat source side unit via described cold-producing medium; And
Cold-producing medium control unit, described cold-producing medium control unit switches the flowing of described cold-producing medium according to operational situation,
Described heat source side unit and described cold-producing medium control unit are connected in series by pipe arrangement, and described cold-producing medium control unit and described load-side unit are connected in series by pipe arrangement, and described load-side unit is connected in parallel by pipe arrangement separately from each other,
Each of described load-side unit performs cooling operation or heats running, and the feature of described conditioner is,
Described heat source side unit has the temperature testing organization for the condensation temperature and evaporating temperature obtaining described cold-producing medium,
The load detecting mechanism of load when described load-side unit has for obtaining running,
According to the load of the described load-side unit using described load detecting mechanism to obtain, change target condensation temperature and the target evaporating temperature of described cold-producing medium,
Control the operating frequency of described compressor and the rotating speed of described pressure fan, to make: the condensation temperature using described temperature testing organization to obtain is consistent with described target condensation temperature, and the evaporating temperature using described temperature testing organization to obtain is consistent with described target evaporating temperature.
2. conditioner according to claim 1, is characterized in that,
Described temperature testing organization
Be made up of the low pressure sensor being arranged on high pressure sensor in described heat source side unit, that detect the discharge pressure of the described cold-producing medium of discharging from described compressor and detection and being inhaled into the suction pressure of the described cold-producing medium of described compressor,
Described condensation temperature is calculated according to the discharge pressure detected by described high pressure sensor,
Described evaporating temperature is calculated according to the suction pressure detected by described low pressure sensor.
3. conditioner according to claim 1 and 2, is characterized in that,
Described load detecting mechanism
Form by being arranged on temperature sensor in described load-side unit, that detect load-side inlet temperature,
The load of described load-side unit is detected according to the difference of described load-side inlet temperature and design temperature.
4. the conditioner according to Claims 2 or 3, is characterized in that,
Whole described load-side unit perform the full heating mode of operation that heats running and
The described load-side unit performing described load-side unit and the execution cooling operation heating running exists simultaneously, and perform large the heating in main body operation mode of each load sum that each load sum ratio heating the described load-side unit of running performs the described load-side unit of cooling operation
Described discharge pressure according to being detected by described high pressure sensor calculates described condensation temperature, and the operating frequency controlling described compressor is to make described condensation temperature consistent with described target condensation temperature,
Described suction pressure according to being detected by described low pressure sensor calculates described evaporating temperature, and the rotating speed controlling described pressure fan is to make described evaporating temperature consistent with described target evaporating temperature.
5. the conditioner according to Claims 2 or 3, is characterized in that,
Whole described load-side unit perform cooling operation full cooling operation pattern and
The described load-side unit performing described load-side unit and the execution cooling operation heating running exists simultaneously, and each load sum performing the described load-side unit of cooling operation is than performing in the large refrigeration main body operation mode of each load sum of heating the described load-side unit of running
Described discharge pressure according to being detected by described high pressure sensor calculates described evaporating temperature, and the operating frequency controlling described compressor is to make described evaporating temperature consistent with described target evaporating temperature,
Described suction pressure according to being detected by described low pressure sensor calculates described condensation temperature, and the rotating speed controlling described pressure fan is to make described condensation temperature consistent with described target condensation temperature.
6. conditioner according to claim 4, is characterized in that,
Described heat source side unit
There is multiple open and close valve and possess the described outdoor heat converter of described pressure fan,
Outdoor heat converter unit is connected in parallel by pipe arrangement each other, and described outdoor heat converter unit to be connected in series through pipe arrangement by described open and close valve and the described outdoor heat converter that possesses described pressure fan and to form,
At described full heating mode of operation and heat in main body operation mode,
Described open and close valve is controlled according to described target condensation temperature.
7. conditioner according to claim 5, is characterized in that,
Described heat source side unit
There is multiple open and close valve and possess the described outdoor heat converter of described pressure fan,
Outdoor heat converter unit is connected in parallel by pipe arrangement each other, and described outdoor heat converter unit to be connected in series through pipe arrangement by described open and close valve and the described outdoor heat converter that possesses described pressure fan and to form,
In described full cooling operation pattern and refrigeration main body operation mode,
Described open and close valve is controlled according to described target evaporating temperature.
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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106801920A (en) * 2017-02-17 2017-06-06 海信科龙电器股份有限公司 A kind of recuperated cycle system and its control method, air-conditioning
CN107036230A (en) * 2016-02-04 2017-08-11 Lg电子株式会社 The method of air-conditioning and control air-conditioning
CN107525217A (en) * 2017-07-27 2017-12-29 青岛海尔空调器有限总公司 A kind of air-conditioner control method, control device and air conditioner
CN107606834A (en) * 2017-09-12 2018-01-19 广东美的暖通设备有限公司 The control method and multiple on-line system of multiple on-line system
CN109114758A (en) * 2018-10-08 2019-01-01 广东美的暖通设备有限公司 Air conditioner system control method and air conditioner
CN109312947A (en) * 2016-11-29 2019-02-05 三菱重工制冷空调系统株式会社 Frigorific unit system, temperature management system, remote controler and control method
CN111023402A (en) * 2019-12-31 2020-04-17 宁波奥克斯电气股份有限公司 Self-adaptive adjusting method of air conditioning system and air conditioner

Families Citing this family (19)

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Publication number Priority date Publication date Assignee Title
US20170121581A1 (en) * 2014-03-17 2017-05-04 Asahi Glass Company, Limited Heat pump apparatus
AU2014387521B2 (en) * 2014-03-20 2016-12-22 Mitsubishi Electric Corporation Heat source side unit and air-conditioning apparatus
JP5967166B2 (en) * 2014-10-22 2016-08-10 ダイキン工業株式会社 Air conditioner
CN104776630B (en) * 2015-04-28 2017-05-03 广东美的暖通设备有限公司 Multi-split system
CN104833010B (en) * 2015-05-25 2017-06-06 广东美的暖通设备有限公司 The outdoor unit and heat-reclamation multi-compressors of heat-reclamation multi-compressors
JP6048549B1 (en) * 2015-08-07 2016-12-21 ダイキン工業株式会社 Refrigeration equipment
JP6444526B2 (en) * 2015-10-20 2018-12-26 三菱電機株式会社 Operation control device
US10760824B2 (en) * 2015-12-17 2020-09-01 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
US11669061B2 (en) * 2016-06-30 2023-06-06 Johnson Controls Tyco IP Holdings LLP Variable refrigerant flow system with predictive control
JP2018013286A (en) * 2016-07-20 2018-01-25 三菱重工サーマルシステムズ株式会社 Control device, air conditioner, and control method
JP6707189B2 (en) * 2017-04-19 2020-06-10 三菱電機株式会社 Air conditioner and fan speed control method for air conditioner
JP6451798B1 (en) * 2017-07-31 2019-01-16 ダイキン工業株式会社 Air conditioner
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CN108375175B (en) 2018-02-08 2019-09-24 珠海格力电器股份有限公司 Air conditioner system control method and device
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EP3859244A4 (en) * 2018-09-28 2021-09-15 Mitsubishi Electric Corporation Air-conditioner
JP6636193B2 (en) * 2019-01-24 2020-01-29 三菱電機株式会社 Abnormality detection system, refrigeration cycle device, and abnormality detection method
US20220082313A1 (en) * 2019-02-28 2022-03-17 Mitsubishi Electric Corporation Refrigeration cycle apparatus
WO2020245918A1 (en) * 2019-06-04 2020-12-10 三菱電機株式会社 Refrigeration cycle device

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101498297A (en) * 2009-02-19 2009-08-05 浙江工业大学 Continuous over loading test system for cold compressor
CN101504177A (en) * 2008-02-05 2009-08-12 Lg电子株式会社 Air conditioning apparatus and method for determining the amount of refrigerant of air-conditioning apparatus
JP4701303B1 (en) * 2010-01-19 2011-06-15 積水化学工業株式会社 Air conditioning system and building
CN102112826A (en) * 2008-06-11 2011-06-29 美国能量变换公司 Method and apparatus for cooling
US20120285675A1 (en) * 2009-12-15 2012-11-15 Mitsubishi Electric Corporation Air-conditioning apparatus

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB849158A (en) * 1955-12-20 1960-09-21 Heat X Inc Refrigeration
JPS5899665A (en) * 1981-12-09 1983-06-14 株式会社システム・ホ−ムズ Heat pump type hot-water supply device
AU636726B2 (en) * 1990-03-19 1993-05-06 Mitsubishi Denki Kabushiki Kaisha Air conditioning system
JP4013318B2 (en) * 1997-07-17 2007-11-28 株式会社デンソー Refrigeration cycle equipment for vehicles
JP4179783B2 (en) * 2002-01-18 2008-11-12 三洋電機株式会社 Air conditioner
US6845629B1 (en) * 2003-07-23 2005-01-25 Davis Energy Group, Inc. Vertical counterflow evaporative cooler
JP4767199B2 (en) * 2007-03-01 2011-09-07 三菱電機株式会社 Air conditioning system operation control method and air conditioning system
CN105180497B (en) * 2008-10-29 2017-12-26 三菱电机株式会社 Conditioner
JP5137933B2 (en) * 2009-11-24 2013-02-06 三菱電機株式会社 Air conditioner
JP5228023B2 (en) 2010-10-29 2013-07-03 三菱電機株式会社 Refrigeration cycle equipment
JP5132757B2 (en) 2010-11-19 2013-01-30 三菱電機株式会社 Control device, control method and program

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101504177A (en) * 2008-02-05 2009-08-12 Lg电子株式会社 Air conditioning apparatus and method for determining the amount of refrigerant of air-conditioning apparatus
CN102112826A (en) * 2008-06-11 2011-06-29 美国能量变换公司 Method and apparatus for cooling
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US20120285675A1 (en) * 2009-12-15 2012-11-15 Mitsubishi Electric Corporation Air-conditioning apparatus
JP4701303B1 (en) * 2010-01-19 2011-06-15 積水化学工業株式会社 Air conditioning system and building

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JP6053826B2 (en) 2016-12-27
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